US3914942A - Servo-assisted fluid supply systems - Google Patents

Servo-assisted fluid supply systems Download PDF

Info

Publication number
US3914942A
US3914942A US469527A US46952774A US3914942A US 3914942 A US3914942 A US 3914942A US 469527 A US469527 A US 469527A US 46952774 A US46952774 A US 46952774A US 3914942 A US3914942 A US 3914942A
Authority
US
United States
Prior art keywords
servo
valve
pressure
amplifier
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US469527A
Other languages
English (en)
Inventor
Juan Simon Bacardit
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AlliedSignal Automotive Espana SA
Original Assignee
Bendiberica SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bendiberica SA filed Critical Bendiberica SA
Application granted granted Critical
Publication of US3914942A publication Critical patent/US3914942A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/101—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic equalising arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/28—Valves specially adapted therefor
    • B60T11/32—Automatic cut-off valves for defective pipes
    • B60T11/323—Automatic cut-off valves for defective pipes in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
    • B60T13/241—Differential pressure systems
    • B60T13/242—The control valve is provided as one unit with the servomotor cylinder
    • B60T13/245—Hydraulic command of the control valve, hydraulic transmission to the brake

Definitions

  • ABSTRACT 30 Foreign Application Priority Data In a fluid pp y y hflving a 9 which M 23, 1973 S 4153 when actuated asslsts the plstons of a plurahty of Indeay Pam 62 pendent amplifier cylinders to deliver working fluid to [52] u Cl. H 60/581, 188/345. 303/21 AF the respective outputs. Actuating means for the servo- 51 Int. c1.
  • the present invention relates to servo-assisted fluid 5 supply systems for supplying working fluid under pressure and in a controlled manner to a plurality of independent outputs.
  • the system may be hydraulic or pneumatic or may employ both media.
  • the invention is particularly though not exclusively applicable to automobile vehicle braking systems.
  • a typical hydro-pneumatic braking system has two or more hydraulic master cylinders delivering fluid to independent brake circuits.
  • the pistons of the master cyll5 inders are connected to a common servo-motor which assists or boosts the effort applied to the pistons by hydraullic fluid supplied by control cylinders.
  • Pneumatic pressure or negative pressure i.e. pressure below atmospheric pressure, is employed to operate the servomotor.
  • Valves actuated by the control cylindrs actuate the servo-motor.
  • a servoassisted arrangement for supplying working fluid under pressure and in a controlled manner to a plurality of independent outputs, wherein independent amplifier cylinders are operated so as to supply working fluid to the respective outputs by control fluid supplied to the amplifier cylinders by respective master cylinders, and a common servo-motor actuated by the control fluid pressure assists the pistons of the amplifier cylinders when the master cylinders are operated, there being provided actuating means for the servo-motor arranged to actuate the servo-motor when the control fluid pressure obtaining in any one of the amplifier cylinders reaches a respective predetermined level.
  • control fluid pressure in another amplifier cylinder can actuate the servo-motor.
  • the master cylinders are actuated in commmon, e.g. by the brake pedal of a vehicle.
  • the actuating means for the servo-motor includes a selector valve having two inlets and an outlet and a shuttle member movable to close off from the outlet either one of its inlets when there exists in that inlet a substantially lower pressure than exists in the other.
  • This selector valve may be arranged with its inlets connected respectively to the outlets of two servovalves actuatable by control fluid pressure in respective ones of the amplifier cylinders to admit operating fluid for the servo-motor to the selector valve and thence to the servo-motor, so that the selector valve closes off either' inlet should operating fluid fail to be applied to that inlet.
  • control fluid pressure obtaining in respective amplifier cylinders may be applied to the selector valve inlets, the outlet being connected to the control inlet of a single servovalve actuable by sufficient fluid pressure in its control inlet to cause operation of the servo-motor.
  • the actuating means for the servo-motor includes a servo-valve actuable to cause the establishment of said pressure difference which operates the servo-motor by fluid applied at sufficient pressure at any one ofa pluralilty of. control inlets of the servo-valve, the control fluid applied to the respective amplifier cylinders being respectivelyv applied to the said control inlets.
  • At least two said outputs are connected to a differential accumulator device having a capacity sufficiently large to compensate for differences in the consumption between the two outputs and sufficiently small not to seriously impair the functioning of one of the outputs if the other fails.
  • FIG. 1 is a diagram illustrating a fluid supply system embodying the invention having two outputs and including two servo-valves in the servo-motor actuating means;
  • FIG. 2 is a diagram illustrating another fluid supply system embodying the invention also having two outputs, but having one servo-valve only;
  • FIG. 3 is a diagram illustrating a third fluid supply system embodying the invention having a servo-valve having two control fluid inlets;
  • FIG. 4 is a view, on an axial section, of one of the servo-valves of the system of FIG. I;
  • FIG. 5 is a view, on an axial section, of the selector valve of the system of FIG. 1;
  • FIG. 6 is a view, on an axial section, of the differential accumulator of the system of FIG. I; 7
  • FIG. 7 is a view, on an axial section of the selector valve of the system of FIG. 2;
  • FIG. 8 is a view, on an axial section, of part of the servo-valve of the system of FIG. 3, the remainder of the valve being similar to the valve shown in FIG. 4.
  • the servo-motor has a cylinder 1 having a piston 2 of the diaphragm or sliding type, which divides the cylinder into two independent working chambers 3, 4.
  • Fast with the piston are two rods 5 extending parallel to the axis of the cylinder 1 and projecting through packings 6, providing fluid-tight seals, and connected to pistons 7, 8 of respective amplifier cylinders 9, 10, there being thus formed in the amplifier cylinders pairs of sealed and independent chambers ll, 12 and I3, 14.
  • Actuation of the master cylinder 19 drives fluid under pressure through the lines 17, 18 to the chambers ll, 13, in such manner as to drive the pistons 7, 8 towards the right in FIG. I.
  • the pistons 7, 8 drive the working fluid in the chambers 12, 14 through the output circuits l5, 16 to the wheel brakes. If failure should take place in either of the two lines 17, 18 or either of the circuits 15, 16, the other circuit continues to be in the operational condition and is able to continue to function until the failure has been remedied.
  • the system as described functions with the power which the master cylinder 19 is able to supply and, consequently, responds to the physical pressure applied by the driver on the brake pedal.
  • the booster cylinder 1 is operated by operating fluid in the form of atmospheric air on one side of piston 2 opposed to negative pressure or vacuum on the other side of the piston 2 obtained from the intake manifold of the vehicle motor, thereby applying additional power to the pistons 7, 8.
  • a conduit 21 extends from the chamber 4 of the cylinder I to the intake manifold 22 of the vehicle engine, downstream of the carburettor or of a throttle valve in the case of deisel engines.
  • the end face of the chamber 4 (the righthand end in FIG. 1) has two large ports 23 (see FIG. 4) which are arranged diametrically opposite each other and in which there are mounted respective switching and modulating servo-valves 24, 25 which together with a selector valve 60 (FIG. 5) comprise actuating means for the servo-motor.
  • the two servo-valves 24, 25 are identical and a description will be given below of only one of them, 24, with reference to FIG. 4. In the description the outer direction is taken to be with respect to the cylinder 1, i.e. towards the right in FIG. 4.
  • the mouth of the port 23 has secured to it by means of screws 26 a part frusto-conical tubular member 27 having within it an intermediate'frusto-conical partition 28 at the narrow end of which there is located an aperture 29 surrounded at the outer side (with respect to the cylinder 1) by an associated valve seat.
  • a valve disc 30 is normally urged against the seat around the aperture 29 by a conical compression spring 31 bearing at its other end against a perforated disc 32 which is retained in position against a step 33 by an expanding ring 34.
  • a filter assembly 35 for filtering the air aspired into the interior of the apparatus during functioning; the assembly 35 is retained in position by a further perforated disc 36 and an associated expanding ring 37, which is readily withdrawn for replacing the filter.
  • the disc 30 is carried by an axial pin 38 which extends through the aperture 29 and carries, within the tube 27 a large obturating disc 39.
  • the screws 26 also secure the periphery of a flexible and impermeable diaphragm designated by the general reference numeral 40 and constituted by a flexible annulus 41, an annular member 42 having an axial passage aperture 43, a valve seat axially outwardly of the aperture 43 for the disc 39, and inwardly of the aperture 43 a perforated dish 44, from which extends axially inwardly an actuating rod 45.
  • a bridge 46 the central portion of which is formed with a blind cavity 47 open towards the above-described diaphragm 40 and formed with an internal screw thread in which is secured a cylindrical member 48 having at its outer end a flange 49 sealed in fluid-tight manner against the outer edge of the said cavity 47, its inner end being slightly spaced from the end face of the cavity 47.
  • a piston 50 mounted for sliding within the cylindrical member 48 is a piston 50 having retaining means 51 and a recess at its forward end which receives the actuating rod 45.
  • a tapered compression spring 52 is compressed between the member 42 and the member 27 in such a manner that it urges the'diaphragm 40 inwardly towardsthe inoperative position shown in FIG. 4, wherein the piston 50 bears against the end face of the cavity 47.
  • the sides of the cavity 47 are formed with grooves 53 establishing communication between the end face thereof and the upper and lower portions thereof. Opening into the upper groove 53 is a purging device 54 which it is assumed is adequately known; into the lower grove 53 debouch'es a conduit 55 extending along the bridge 46 and communicating, via the body of the device, with the chamber 11 or 13 of the respective adjacent clyinder 9 or 10.
  • the conduit 55 is the control inlet of the valve.
  • the valve 24 thus has two inlets, viz. a first inlet 23 and a second inlet from the atmosphere through the filter 35, to its chamber 56 delimited between the diaphragm 40 and the partition 28, from which extends on outlet conduit 57 the purpose of which will be described later.
  • the outlet conduits 57 of the two valves 24, 25 are connected, respectively. to the two inlets 58, 59 ofa selector or differential valve means 60 shown in FIG. 5, which has a single oulte 61 communicating with the chamber 3 of the cylinder 1.
  • a selector or differential valve means 60 shown in FIG. 5, which has a single oulte 61 communicating with the chamber 3 of the cylinder 1.
  • Formed within the valve 60 are two opposed frusto-conical seats 62, 63 against either one of which there is arranged to close a shuttle member in the form of a ball 64 freely movable within the valve.
  • the nega tive pressure obtaining in the chamber 4 passes through the aperture 43, the chamber 56, the conduit 57 and the valve 60 to the chamber 3, in such manner that the piston 2 is subjected to equilibrated pressures and is held by a helical spring 65 (FIG. 4) displaced to the maximum extend'towards the left in FIG. 1.
  • the disphragm 40 is thus deformed towards the right.
  • the member 42 applies the seat surrounding its aperture 43 against the disc 39 in such manner as to interrupt communication between the chamber 56 and the chamber 4, i.e. in effect between the two chambers 3 and 4;
  • the continuing movement towards the right of the diaphragm 40 then moves in the same direction the assembly constituted by the pin 38 and the two valve discs 39, 30, thus opening aperture 29 to establish communication between the chamber 56 and the atmosphere, ie. to allow flow of atmospheric air, the operating fluid of the cylinder 1, to the chamber 3.
  • the chamber 4 is under negative pressure, a pressure difference is established across the piston 2, which is displaced to the right and applies, through the rods 5, a corresponding force to the pistons 7, 8.
  • the diaphragm 40 compares the actuating pressure with the atmospheric pressure, in such manner that with variation of the former there is obtained corresponding modulation of the braking pressure.
  • the pistons of the master cylinder 19 travel back, in such manner as to reduce the hydraulic pressure in the cylinders 48 controlling the servo-valves 24, 25.
  • the springs 52, 31 displace the movable assemblies of the said valves towards the left, in such manner that first the passage 29 is closed, thereby interrupting communication of the chamber 56, i.e. of the chamber 3 in the cylinder 1, with the atmosphere; then, the passage 43 is opened, whereby the chamber 56 is connected to the chamber 4 and negative pressure is restored to the chamber 3; the pressures on both faces of the piston 2 are equalised and the spring 65 displaces the pistons 2, 7, 8 towards the left, into the inoperative position.
  • the usual safety feature is provided, inasmuch as they are independent of the associated circuits l5, 16. If failure should occur in either one of the lines l7, 18, the valve 24, 25 respectively will not be actuated and its outlet conduit 57 will be maintained under negative pressure. With the arrangement of the invention the atmospheric pressure arriving at the valve 60 via the conduit 57 of the other pneumatic valve will apply the ball 64 against one of the seats 62, 63 to block the inoperative inlet, so that the servo-valve which is maintained in operation actuates the servo-.
  • a differential hydraulic accumulator device 66 shown in detail in FIG. 6, is connected asshown in FIG.
  • the accumulator 66 may not absorb a detrimentally large portion of the cylinder content impelled by the master cylinder 9 or 10 associated with the circuit which is still functioning.
  • FIG. 2 shows a simplified variant of the system of FIG. 1 described, which functions in accordance with the same working principles. Corresponding elements have been given the same reference numerals. For the sake of convenience, in this case there has not been shown the double master cylinder 19, nor the intake manifold 22. The difference is that one of the hydropneumatic servo-valves (specifically the servo-valve 24) has been dispensed with, so that energisation of the chamber 3 by atmospheric air pressure is effected directly by the outlet conduit 57 of the single valve 25, these being no pneumatic selector valve 60.
  • the hydropneumatic servo-valves specifically the servo-valve 24
  • Control fluid pressure to control the servo-valve 25 is applied to the control inlet 55 via a conduit 73 from the outlet of an hydraulic selector valve 74, the two inlets of which are connected by means of the conduits 75, 76 respectively with the chambers 11, 13 of the master cylinders 9, 10.
  • the selector valve 74 is shown in detail in FIG. 7 and comprises a cylinder 77 sealed at its two ends into which debouch the conduits 75, 76 mentioned hereinabove and which is formed with a central port from which extends the outlet conduit 73.
  • a shuttle member mounted for slid ing within the said cylinder 77 is a shuttle member in the form of a free piston 78 which is rendered fluidtight by a toroidal packing 79 and the faces of which each carry an obturating means 80 disposed to seal the conduits 75, 76 respectively.
  • a helical spring 81 maintains the piston displaced towards one of the ends, in such manner that one of the inlets is normally closed.
  • FIG. 3 is analagous to the cm hodimcnt described with reference to FIG. 2, with the difference that the hydraulic selector valve 74 is replaced by a different form of selector device located in the servo-valve itself, though the general mode of functioning is the same and corresponding parts are again denoted by the same reference numerals.
  • the actuating member 82 (equivalent to piston 50 of FIG. 4) has an intermediate step 83 affording a stop for a piston 84 slidably disposed on the rod 82 and bearing against a washer 85 and axially separated from a piston 86 which is fast with the said rod 82.
  • conduit 75 conveying the control fluid applied to amplifier cylinder 9, debouehes into the chamber 47 as in FIG. 4 to act directly on the piston 84
  • the other conduit 76 conveying the control fluid pressure applied to cylinder 10 debouehes into a recess 87 from which a port 88 formed in the cylinder 48 leads to the space between the two pistons 84, 86.
  • a toroidal packing 89 around the cylinder 48 isolates the two circuits from each other in case of failure of one of them.
  • the plurality of amplifier cylinders 9 and 10 which are respectively connected to the plurality of output circuits l5 and 16, respectively have their pistons 7 and 8 connected to a common piston 2 of a servo-means l, 2 which thus is common to the plurality of amplifier cylinder means 9, l0.
  • Fluid under pressure is supplied to the plurality of amplifier cylinder means 9, 10 from a suitable source which in the illustrated example is the master cylinder means 19, the fluid being supplied through the conduits 17 and 18.
  • At least one servo-valve means 25 is operatively connected with the servo means 1, 2 for normally maintaining equal pressures on opposite sides of the servo piston 2, these equal pressures preferably being less than atmospheric pressure as a result of the connection of the cylinder 1 to the manifold 22 by way of the pipe 21.
  • the component 21, 22 form a source of vacuum for providing less than atmospheric pressure in the servo cylinder 1.
  • the servo valve means 24 is operatively connected with the plurality of amplifier cylinder means 9, 10 to respond automatically to an increase in fluid pressure delivered to the amplifier cylinder means 9, 10 from the source means 19 in order to maintain less than atmospheric pressure on one side of the servo piston 2 while providing an increased pressure on the other side of the piston 2, the latter increased pressure being derived from a source of fluid pressure greater than the equalized pressure normally maintained on opposite sides of the piston 2, and this source of fluid under greater pressure is the atmosphere in the illustrated example.
  • a selector means is operatively connected with at least the servo-valve means 25 for automatically operating the latter with the increased fluid pressure of whichever one of the amplifier cylinders 9, 10 receives from the source means 19 fluid under pressure which reaches a pressure ofa given magnitude.
  • This selector means may take the form either of the valve structure 60 shown in FIG. 5, the valve structure 74 shown in FIG. 7, or the selector structure shown in FIG. 8 and formed by the pistons 84 and 86 which operate in the manner described above.
  • a fluid pressure system supply source means for supplying fluid under pressure
  • a plurality of amplifier cylinder means respectively communicating with said supply source means for receiving fluid under pressure therefrom
  • said plurality of amplifier cylinder means respectively having pistons therein
  • servo means common to said plurality of amplifier cylinder means and including a servo piston operatively connected with the plurality of pistons of said plurality of amplifier cylinder means
  • said servo means including a single servo cylinder housing said servo piston and defining therewith a pair of chambers respectively situated on opposite sides of said servo piston
  • a relatively low fluid pressure source communicating with one of said chambers
  • servo-valve means communicating with said plurality of amplifier cylinder means, with said chambers of said servo cylinders and with a relatively high fluid pressure source of fluid at pressure substantially higher than the pressure of the fluid of said relatively low pressure source which communicates with said one chamber, for normally maintaining pressures in both chambers on opposite sides of said servo piston equalized at the pressure of said relatively low fluid
  • said servo-valve means includes a plurality of servo-valves respectively communication with said plurality of amplifier cylinder means and each communicating with said relatively high fluid pressure source, said selector means being connected between said plurality of servovalves and said other chamber for providing communication between said other chamber and at least one of said servo-valves which communicates with an amplifier cylinder means having therein a pressure which reaches said predetermined value.
  • said servo-valve means includes a single servo-valve communieating with said plurality of amplifier cylinder means and said selector means being connected between said plurality of amplifier cylinder means and said single servo-valve for operating the latter with pressure from at least one amplifier cylinder means wherein the pressure reaches said predetermined value.
  • said servo-valve means includes a single servo-valve communicating with said plurality of amplifier cylinder means, said selector means including in said servo-valve a single cylinder and a plurality of pistons in said single cylinder and respectively communicating through said single servo-valve with said plurality of amplifier cylinder means so that at least one of the latter pistons can respond to fluid pressure in at least one amplifier cylinder means which reaches said predetermined value for actuating said servo-valve.
  • a differ ential accumulator means communicates with said plurality of output circuits for compensating for differences in consumption of fluid by said plurality of output circuits while having a capcity small enough not to impair the functioning of one of said output circuits if another one fails.
  • said source of relatively high pressure is the outer atmosphere while said source of relatively low pressure pro vides less than atmospheric pressure
  • said servovalve means having an outer portion communicating with the outer atmosphere, an inner portion communicating with said one chamber, and an intermediate portion situated between said outer and inner portions and communicating with said other chamber, an outer normally closed valve situated between said outer and intermediate portions for normally preventing communication between the outer atmosphere and said intermediate portion, and an inner normally open valve providing normally communication between said intermediate and inner portions for normally maintaining said chambers on opposite sides of said servo piston at an equalized pressure equal to the pressure of said relatively low fluid pressure source
  • said servo-valve means including a cylinder communicating with at least onoe of said amplifier cylinder means and a piston in the latter cylinder operatively connected with said inner and outer valves for closing said normally open inner valve and opening said normally closed outer valve when fluid under pres sure in said one amplifier cylinder means acts on said piston in said cylinder of said servo-valve means upon reaching a pressure equal to said predetermined value.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Fluid-Pressure Circuits (AREA)
US469527A 1973-05-23 1974-05-13 Servo-assisted fluid supply systems Expired - Lifetime US3914942A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ES415362A ES415362A1 (es) 1973-05-23 1973-05-23 Perfeccionamientos en aparatos elevadores de potencia para sistemas de fluido a presion con varias salidas de presion independientes entre si.

Publications (1)

Publication Number Publication Date
US3914942A true US3914942A (en) 1975-10-28

Family

ID=8464288

Family Applications (1)

Application Number Title Priority Date Filing Date
US469527A Expired - Lifetime US3914942A (en) 1973-05-23 1974-05-13 Servo-assisted fluid supply systems

Country Status (6)

Country Link
US (1) US3914942A (enExample)
DE (1) DE2420685A1 (enExample)
ES (1) ES415362A1 (enExample)
FR (1) FR2230886B1 (enExample)
GB (1) GB1471439A (enExample)
IT (1) IT1011743B (enExample)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4351153A (en) * 1976-03-05 1982-09-28 Kosmala Rupert M Hydraulic control device
US6879103B1 (en) 1997-03-18 2005-04-12 The Trustees Of The Stevens Institute Of Technology Glow plasma discharge device
US20150035350A1 (en) * 2013-07-31 2015-02-05 Bendix Spicer Foundation Brake Llc Biased Double Check Valve for Brake System

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2526570A (en) * 1945-11-05 1950-10-17 Warner Aircraft Corp Compensator for independent fluid pressure systems
US3173261A (en) * 1961-03-08 1965-03-16 Automotive Prod Co Ltd Fluid pressure braking systems
US3550377A (en) * 1968-02-15 1970-12-29 Toyoju Mochinzuki Intensifier for dual system power brakes
US3706479A (en) * 1967-09-26 1972-12-19 Teves Gmbh Alfred Nonskid brake system for motor vehicle with pressurized hydraulic system
US3760912A (en) * 1970-09-18 1973-09-25 Porsche Kg Safety system for two-circuit brake installations of motor vehicles

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2149265B1 (enExample) * 1971-08-13 1975-08-29 Teves Gmbh Alfred

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2526570A (en) * 1945-11-05 1950-10-17 Warner Aircraft Corp Compensator for independent fluid pressure systems
US3173261A (en) * 1961-03-08 1965-03-16 Automotive Prod Co Ltd Fluid pressure braking systems
US3706479A (en) * 1967-09-26 1972-12-19 Teves Gmbh Alfred Nonskid brake system for motor vehicle with pressurized hydraulic system
US3550377A (en) * 1968-02-15 1970-12-29 Toyoju Mochinzuki Intensifier for dual system power brakes
US3760912A (en) * 1970-09-18 1973-09-25 Porsche Kg Safety system for two-circuit brake installations of motor vehicles

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4351153A (en) * 1976-03-05 1982-09-28 Kosmala Rupert M Hydraulic control device
US6879103B1 (en) 1997-03-18 2005-04-12 The Trustees Of The Stevens Institute Of Technology Glow plasma discharge device
US20150035350A1 (en) * 2013-07-31 2015-02-05 Bendix Spicer Foundation Brake Llc Biased Double Check Valve for Brake System
US9156456B2 (en) * 2013-07-31 2015-10-13 Bendix Spicer Foundation Brake Llc Biased double check valve for brake system

Also Published As

Publication number Publication date
ES415362A1 (es) 1976-02-01
GB1471439A (en) 1977-04-27
DE2420685A1 (de) 1974-12-12
IT1011743B (it) 1977-02-10
FR2230886B1 (enExample) 1979-07-06
FR2230886A1 (enExample) 1974-12-20

Similar Documents

Publication Publication Date Title
US4050748A (en) Braking system having anti-skid control
US2532960A (en) Brake booster
SE448975B (sv) Anordning for reglering av bromsslirning med hjelpenergimatning
US4130990A (en) Hydraulic system for feeding a plurality of independent hydraulic servo-operated devices
GB1373196A (en) Tandem spring and service brake actuator
US3789611A (en) Brake valve for a hydraulic brake installation
US3813992A (en) Dual fluid pressure motor
US3958495A (en) Air-oil amplifier
US3564849A (en) Pneumatic booster assembly for brake system
US4116492A (en) Brake valve arrangement for a two-circuit brake system
US3442080A (en) Dual hydraulic brake systems and brake booster mechanisms therefor
GB1183825A (en) Improvements in or relating to Hydraulic Systems.
US2441050A (en) Fluid pressure brake system for tractor-trailer vehicles
US3800540A (en) Double master cylinder
US3914942A (en) Servo-assisted fluid supply systems
US2852921A (en) Booster brake mechanism
US3165031A (en) Hydraulic brake booster
US2406328A (en) Power brake mechanism
US4109967A (en) Brake-force distributor for dual-circuit brake systems
US4073543A (en) Switching device for the indirect alteration of the mechanical brake pedal transmission
JPH0535900Y2 (enExample)
US2737777A (en) Hydraulic brake booster
US4220375A (en) Braking pressure control unit
US3183670A (en) Power brake means
US2434050A (en) Tractor-trailer brake system